Winder



Aug. 9, 1966 E. e. MUELLER WINDER Filed July 29, 1963 5 Sheets-Sheet l INVENTOR Y EDWARD e. MUELLER ATTORNEY S Aug. 9, 1966 E. G. MUELLER WINDER Filed July 29. 1963 5 Sheets-Sheet 2' 4. III! llll'l'f LLII INVENTOR EDWARD G. MUELLER BY 23%, fmLm ATTORNEYS Aug. 9, 1966 E. G. MUELLER 3,255,315

- I WIND'ER Filed July 29, 196 5 Sheets-Sheet s- INVENTOR EDWARD G. MUELLER ATTORNEY6 INVENTOR EDWARD G. MUELLER 5 Sheets-Sheet 4 WINDER BY @VM, flrlb/n9 774412 ATTORNEY 5 E. G. MUELLER Aug. 9, 1966 Filed July 29, 1965 E. G. MUELLER Aug. 9, 1966 WINDER s Sheets-Sheet 5 Filed July 29. 1963 o o m INVENTOR EDWARD G. MUELLER ATTORNEYS United States Patent 3,265,315 WINDER Edward G. Mueller, Huntingdon Valley, Pa., assignor, by mesne assignments, to Maremont Corporation, Chicago, 111., a corporation of Illinois Filed .luly 29, 1963, Ser. No. 298,040 23 Claims. (Cl. 242-18) This invention relates to machines for winding thread, yarn, wire, and other strand material onto cops, cones,

spools, and other packages. More specifically, this invention relates to Winding machines having a winding spindle or member supporting a package on which the strand is wound, a reciprocable guide for guiding the thread onto the package, and a gainer mechanism for displacing successive wraps of thread to form a stable thread package.

Winding machines answering this general description are well known. Exemplary United States patents disclosing such machines are Nos. 2,296,959, issued to E. R. Swanson, September 29, 1942, for Winding Machine; 2,028,679, issued to W. Marcroft, January 21, 1936, for Winding Machine; and 2,079,730, issued to H. R. Blair, May 11, 1937, for Gainer Mechanism for Winding Machines.

The prior art winders, as shown by the above patents, are large, bulky machines. This characteristic is highly undesirable in many modern installations where winders are employed in batteries of fifty or a hundred or even more.

It is, therefore, one object of the present invention to provide novel winding machines which are substantially more compact than those of the prior art,

This object is fulfilled by a novel construction in which a cylindrical cam having a closed helical cam track is employed in place of the conventional, large diameter, bulky thread guide cams illustrated in the exemplary patents referred to above to reciprocate the thread guide. Further compactness is achieved by supporting the thread guide reciprocating assembly in which the cam is incorporated and the package supporting winding spindle in cantilever fashion from a casting housing the gainer mechanism in side-by-side relationship with each other and the motor of the winding machine.

A further reduction in bulk is achieved by connecting the follower reciprocated by the thread guide reciprocating cam directly to the arm on which the thread guide is mounted. In addition to making the winders of the present invention more compact, this novel feature materially reduces the complexity of the thread guide reciprocating mechanism, providing a much simpler mechanism than that shown in the above-listed exemplary patents.

In conjunction with the foregoing, the winding machines of the present invention employ a novel power train which materially contributes to their compactness. As shown by copending application No. 138,166, filed September 14, 1961, by August I. Hambach for Precision Winders, the most modern of the prior art winders are driven by electric motors provided with two oppositely extending output shafts. The winding spindle is fixed to one of the output shafts; and the thread guide reciprocating cam is drive-connected to the other through a gainer mechanism. The power train of the present invention eliminates the necessity of employing dual motor shafts and makes it possible to drive both the winding spindle and the gainer mechanism from a single motor shaft. This arrangement is alsoimportant in that single shaft motors are substantially less expensive than those of the dual shaft type.

In addition to compactness and simplicity, other important advantages are obtained by the novel Winder construction discussed above. For example, in the winders disclosed in the above copending Hambach application,

the thread guide reciprocating mechanism is supported by the two end members of a three-piece winder casting. This often presents some difiiculty in maintaining the thread guide reciprocating mechanism in proper alignment. In the winders of the present invention problems in maintaining the thread guide reciprocating mechanism in alignment are eliminated by employing a unitary casting and the cantilevered guide reciprocating mechanism discussed above.

A further feature of the present invention is a novel mechanism by which the force with which the thread guide is biased against the thread package may be selectively manually varied. This permits the biasing force to be adjusted to the optimum for different kinds of threads and for various sizes and types of packages, for example.

Among the important additional objects of the invention described above are the following:

(1) The provision of materially improved thread winders;

(2) The provision of novel thread winders which are more simple than those of the prior art;

(3) The provision of novel, improved, thread guide reciprocating mechanisms;

(4) The provision of novel, improved, thread winder drive trains;

(5) The provision of novel thread winders in which problems related to the alignment of the thread guide reciprocating mechanism are eliminated;

(6) The provision of thread winders having a novel mechanism for selectively manually varying the force with which the thread guide is biased against the thread package; and

(7) The provision of novel thread winders which are substantially more economical to manufacture and to maintain than those of the prior art.

Additional objects and further novel features of the present invention will become more fully apparent from the appended claims and as the ensuing detailed discussion and description proceeds in conjunction with the accompanying drawing, in which:

FIGURE 1 is a perspective view of a thread winding machine constructed in accordance with the principles of the present invention;

FIGURE 2 is a right-hand end view of the thread winding machine illustrated in FIGURE 1, with the cover of the gainer mechanism housing removed;

FIGURE 3 is a plan view, partly in section, of the thread winding machine of FIGURE 1;

FIGURE 4 is a vertical section through the thread guide reciprocating mechanism employed in the thread winding machine of FIGURE 1;

FIGURE 5 is a section through the thread guide reciprocating mechanism, taken substantially along line 5-5 of FIGURE 4;

FIGURE 6 is a plan view, partly in section, of the thread guide assembly employed in the thread winding machine of FIGURE 1;

FIGURE 7 is a vertical section through the thread guide assembly, taken substantially along line 77 of FIGURE 6; and

FIGURE 8 is a vertical section through the thread guide assembly, taken substantially along line 8-8- of FIGURE 6.

Referring now to FIGURES 1-3, thread winding machine Ztl, constructed in accordance with the principles of the present invention, includes a rotatable winding spindle 22 on which a thread package 24 is mounted. Thread is guided onto package 24 by a reciprocating thread guide assembly winding spindle 22 and the reciprocating thread guide assembly 26 are driven by a motor 30 drive-connected to the winding spindle by a belt drive 32. Winding spindle 22 is drive-connected, through a gear type gainer mechanism 34, to a thread guide reciprocating mechanism 36 by which the thread guide assembly 26 is reciprocated.

Winding machine motor 30 is an especially designed single phase or polyphase electric motor which automatically slows down as the diameter of the material builds up on the thread package to maintain uniform tension and winding speed. Suitable motors having the foregoing characteristics are manufactured by the A. B. Wesche Electric Company of Cincinnati, Ohio. The performance characteristics of these motors are discussed in an article entiled Torque Motors and Brakes printed in the April 1957 issue of Product Engineering and in the copending Hambach application referred to above.

Winding machine motor 30 is fixed in any convenient manner to and is supported in cantilever fashion from the vertical wall 38 of a unitary casting 4t hereinafter referred to as the gainer mechanism housing.

Turning now to FIGURES 2 and 3, thread winding machine motor 30 has a single output shaft 46, extending into gainer mechanism housing 40, to which a drive pulley 48 is fixed as by a key 50. A flexible drive belt 52 extends around pulley 48 and around a driven pulley 54 (see especially FIGURE 3) keyed or otherwise rotatably fixed to winding spindle 22. The tension on drive belt 52 may be varied by adjusting the position of an idler pulley 56, journalled on a stub shaft 58 which is fixed to a wedge-shaped support plate 60.

Support plate 60 is pivotally mounted on the vertical side wall 38 of gainer mechanism housing 40 as by a pivot stud 62 and is provided with an arcuate slot 64 adjacent the end thereof opposite stub shaft 58. A bolt 66, extending through slot 64 into threaded engagement with gainer mechanism housing side wall 38, may be tightened to retain idler pulley 56 in the position to which it is adjusted.

Referring now specifically to FIGURE 3, winding spindle 22 is an elongated shaft rotatably supported by a pair of axially spaced apart roller bearings 68 and 70 located in an integral apertured boss 72 oriented normal to gainer mechanism housing vertical side wall 38 and located above motor 30. Suitable seals 74 and 76 are located adjacent bearings 68 and '70 to prevent lubricant from leaking to the exterior of gainer mechanism housing 40.

As best shown in FIGURE 3, cylindrical package supports 78 and 80 are mounted on the inboard and outboard ends of winding spindle 22 to support package 24 which, as illustrated, is a cylindrical cardboard tube although any desired type of package may be used. Radial flanges 82 on the package supports provide axially extending circular projections 84 which maintain package 24 in concentric relation with the winding spindle 22 and annular projections 86 which maintain the package in a fixed axial relation to the winding spindle.

The inboard package support 78 is fixed to Winding spindle 22 as by a setscrew 88. Outboard package sup port 80 is removably retained in place by a knob 90 provided with a shank 92 threaded into the outboard end of the winding spindle. By unscrewing knob 90, outboard package support 80 may be removed, permitting the package to be doffed from the winding spindle.

To prevent the thread being wound onto package 24 from becoming entangled with the winding machine mechapism, a conical yarn guard 94, which surrounds the inboard end of winding spindle 22, is fixed to gainer mechmechanism 34. Input gear 98 meshes with a spur gear 104 which, together with a spur gear 106, form an intermediate gear assembly 188. Intermediate gears 104 and 106 are fixed together for concomitant rotation and are rotatably supported by a stub shaft 110 on which they are secured by a wing nut 112. Stub shaft 110 extends normally from and is fixed to an intermediate gear assembly support bracket 114 fixed to gainer mechanism housing side wall 38 by a cap screw 116 which extends through a washer 118 and an elongated slotted aperture 120 in bracket 114 into threaded engagement with the housing side wall. The elongated slot 120 permits universal movement of support bracket 114 in a plane parallel to the gainer mechanism gears, permitting gears of varying diameter to be mounted on stub shaft 110 and moved into meshing engagement with the cooperating gears of the gainer mechanism. Bracket 114 is retained in the position to which it is adjusted by tightening cap screw 116.

Gear 106 of intermediate gear assembly 108 meshes with a spur gear 122 fixed to the end of a camshaft 124 by a key (not shown) and a wing nut 128. In a manner which will be described in detail presently, the rotation of cam shaft 124 efiects reciprocation of thread guide assembly 26 axially of thread package 24 to guide the thread onto the package. The gainer mechanism so relates the simultaneous rotation of thread package 24 and reciprocation of thread guide assembly 26 that one wrap of the thread guided onto the package will not be laid exactly on top of the preceding wrap as this would produce a highly unstable package. The functions of gainer mechanisms and the manner in which they operate are described in detail in the copending Hambach application identified above to which reference may be had if deemed necessary for an understanding of the present invention.

One of the important features of the gainer mechanism described above is that the gears may be quickly and easily replaced by the operator to change the gain and/ or point wind. This may be done in only about one-twentieth of the time required to perform the same operation in competitive winders.

As indicated above, the housing 48 surrounding gainer mechanism 34 is a unitary casting provided with a vertical side wall 38. Housing 40 has a second integral vertical side wall 132 disposed in parallel spaced relationship to side wall 38. An enlarged opening 134 is provided in housing side wall 132 to permit access to gainer mechanism 34. Access opening 134 is closed by a cover 136 bolted, or secured in any other desired manner, to the gainer mechanism housing.

Apertured bosses 138, formed on the lower wall 140 of housing 48, permit thread winding machine 20 to be bolted to a suitable support. A lifting eye 142 is threaded into an apertured boss 144 formed on the top wall 146 of gainer mechanism housing 40 to facilitate movement of thread winding machine 20.

Referring now to FIGURES 3 and 4, the camshaft 124 rotated by the gainer mechanism is fixel to the inboard end of an elongated, cylindrical cam 148 in the surface of which a closed, helical groove or cam track 150 is formed. In the illustrated embodiment, cam 148 is 2.5 inches in diameter and 12 inches long. Cam track 150 is five-wrapped; i.e., the track makes five circumvolutions of cam 148. As a result, a cam follower will move rectilinearly from one to the other of the two ends of cam 148 once in every five revolutions of the cam.

The precise dimensions of cam 148 and the number of circumvolutions of cam track 150 are not critical. However, in order to produce a stable package, the'ratio of the length of the cam to. the cam diameter multiplied by the number of circumvolutions should be approximately 1 to 1.

Cam 148 is rotatably supported in a housing 152 by a ball bearing 154 disposed in the apertured inboard end wall 156 of the housing and by a ball bearing 158 which surrounds a stub shaft 160 fixed to the outboard end of cam 148. Ball bearing 158 is disposed in an aperture 162 formed in an end plate 164 fixed to the outer end of traverse mechanism housing 152 as by shoulder screws 166.

Cam 148 is axially located in housing 152 by an adjustable collar 168 fixed (after adjustment) on stub shaft 160 between the outboard end of cam 148 and ball bearing 158 as by a setscrew (not shown). An O-ring type seal 170 located between housing 152 and end plate 164 prevents lubricant from leaking to the exterior of the housing.

The rotation of cylindrical cam 148 moves a cam follower 172 rectilinearly along a path parallel to the longitudinal axis of the cam. Cam follower 172 includes a uniformly thick, enlarged width lower portion 174 which depends into cam track 150 and an upwardly directed stem 176 which extends into a downwardly opening cylindrical blind aperture 178 in a block-like cam follower support 181). Cam follower 1'72 and cam follower support 180 are fixed for concomitant movement, but the cam follower may pivot relative to its support to follow cam track 158.

As shown in FIGURE 5, cam follower support 180 is disposed in an opening 182 formed in the top of traverse mechanism housing 152 and extending the length thereof. A slotted dust cover 184 is secured over top opening 182 as by screws 186 (see FIGURE 5). Lateral flanges 188, formed on the lower end of cam follower support 180, cooperate with dust cover 184 to prevent dust from penetrating to the interior of traverse mechanism housing 152.

Alternatively, a slitted plastic or rubber membrane may be employed as a dust cover. In this case, the follower support will push the membrane aside as it reciprocates.

Referring next to FIGURES 4 and 8, cam follower support 180 is fixed by cap screws 189 to a short, generally cylindrical thread guide assembly support 190 slidably supported on an elongated guide bar 192 by bearings 193 which may be of any desired type and are retained in place by snap rings 194. Guide bar 192 is supported in parallel spaced relationship to cylindrical cam 148 by reduced diameter end portions 195 which extend into apertures 196 in, respectively, housing inboard end wall 156 and the end plate 164 attached to the outboard end of the housing.

The thread guide assembly 26, by which the thread is guided onto package 24, includes an elongated arm 198, preferably cast from aluminum or other lightweight material, and pivotally mounted, at one end, on. the reciprocal cylindrical support 190. Thread guide assembly arm 198 is prevented from moving axially of support 190 as by snap rings 200.

A pigtail type thread guide 202 is threaded into the rear, or pivoted, end of thread guide assembly arm 198 and is retained in place by a nut 203. A preferably ceramic thread guide insert 204 is fixed to the forward or free end of thread guide assembly arm 198 by a machine screw 206 as shown in FIGURES 6 and 7. Thread guide insert 204 may but need not necessarily be of the type illustrated in FIGURE 1 of the above-identified Harnbach application.

Referring now to FIGURES 6 and 7, a spring biasing assembly 208 is provided in thread guide assembly 26 to maintain thread guide insert 294 in contact with thread package 24. Assembly 208 includes a flat spring 210 fixed, at one end, between cam follower support 180 and reciprocable thread guide assembly support 190 by the cap screws 139 which connect the two supports. Spring 210 is wrapped around, and fixed at its opposite end, in a slotted sleeve 212 fixed to a horizontally extending shaft 214 rotatably supported in aligned apertures 218 and 220 formed in thread guide assembly arm 193. An adjusting knob 222 is fixed to the outer end of shaft 214.. By rotating knob 222, spring 210 can be wound or unwound,

6 changing the force exerted by spring 219 on thread guide assembly arm 198 and, consequently, the force with which thread guide insert 204 is biased against package 24.

To retain shaft 214 in the position to which it is adjusted, a ratchet 224 and a pawl 226 are employed. Ratchet 224 is rotatably fixed to shaft 214 by a set pin 228. Pawl 226, which is preferably a short length of spring metal, is fixed, at its upper end, to a depending projection 229 on thread guide assembly arm 198 by a screw 230 and nut 232. The lower end of pawl 226 depends into engagement with the teeth 234 on ratchet 224.

The thread guide reciprocating mechanism 36 and thread guide assembly 198 are supported in cantilever fashion from vertical side wall 38 of gainer mechanism housing 40 above and to the same side of motor 30 as winding spindle 22 and in parallel, spaced, side-by-side relationship to the thread winder motor and winding spindle by cap screws 236. The cap screws extend through apertures 238 in an annular flange 240 formed on the inboard end wall 156 of housing 152 into threaded engagement with the gainer mechanism housing side wall 38.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiment is therefore to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by Letters Patent is:

1. A thread winding machine comprising a motor, a gainer mechanism operably connected to said motor, rotatable means for supporting a package adapted to have a thread wound thereon drive-connected to said motor, reciprocable means for guiding a thread onto said package, means including a rotatably mounted cam driveconnected to said gainer mechanism for reciprocating said thread guiding means, and a gainer housing surrounding said gainer mechanism, the axial centerlines of said cam and said package supporting means being fixed relative to each other, and said thread package supporting means, said cam, and said motor being fixed to and supported from said gainer housing.

2. The thread winding machine as defined in claim 1, wherein the diameter of said rotatably mounted cam multiplied by the number of revolutions said cam makes for each traverse of said follower is substantially equal to the length of said cam.

3. The thread winding machine as defined in claim 1, wherein said cam has a multiple-wrapped, closed, helical cam track formed in its surface.

4. The thread winding machine as defined in claim 1, wherein said thread guiding means includes an elongated arm rotatably journalled at one end on a reciprocable support, a thread guide fixed to the other end of said arm, and means for biasing said guide against the thread package with a selectively adjustable force comprising a member rotatably journalled in said arm and a spring coiled around said member, said spring being operatively connected at one end to the rotatable member and at the other to said support.

5. The thread winding machine as defined in claim 4-, including a ratchet fixed to said rotatable member and a pawl fixed to said arm and extending into engagement with the teeth of said ratchet to retain said member in the position to which it is adjusted.

6. The thread winding machine as defined in claim 1, V

wherein the axial centerlines of said cam and said package supporting means both lie to the same side of the vertical plane including the axial centerline of the motor output shaft.

7. The thread winding machine as defined in claim 1, wherein the axial cen-terlines of said cam and said package supporting means are above and substantially parallel to the output shaft of said motor.

8. A thread winding machine comprising a motor having an output shaft, rotatable means for supporting a thread package adapted to have a thread wound thereon and av gainer mechanism both drive-connected to said motor outputrshaft, a housing surrounding said gainer mechanism, and means for guiding a thread onto the package including a thread guide reciprocating assembly including a rotatably mounted cam drive-connected to the gainer mechanism, said assembly being supported in cantilever fashion from said housing and the axial centerines of said rotatable thread package supporting means, said cylindrical cam and said motor output shaft being immovably fixed relative to each other.

9. The thread winding machine as defined in claim 8, wherein said package supporting means includes a shaft supported in cantilever fashion from said housing.

10. The thread winding machine as defined in claim 9, including a pair of bearings spaced axially of the shaft of said package supporting means adjacent the supported end thereof, said bearings being interposed between said housing and said last-named shaft to permit free rotation of said shaft and to prevent axial, transverse, and twisting movement of the shaft relative to the housing.

11. The thread winding machine as defined in claim 1, wherein said gainer mechanism includes an input gear fixed to said rotatable package supporting means and including a belt drive-connecting the motor to the package supporting means.

12. The thread winding machine as defined in claim 11, including a selectively manually adjustable idler pulley pivotally supported from the gainer housing for adjusting the tension in said belt.

13. The thread winding machine as defined in claim 11, wherein said gainer mechanism further comprises an output shaft, an output gear fixed to said output shaft, and a gear assembly comprising a pair of axially aligned, rotatably fixed intermediate gears of dissimilar pitch diameter, said intermediate gears being in operative engagement with, respectively, said input gear and said output gear.

14. The thread winding machine as defined in claim 13, including a member mounted for universal move ment in a plane normal to the axis of alignment of the members of said gear assembly, means mounting said gear assembly means on said member, and selectively operable means for maintaining said member immovable after the gears of said gear assembly have been positioned in operative relationship with said input gear and said output gear.

15. The thread winding machine as defined in claim 14, wherein the gainer housing has a vertical side wall, said package supporting means, said gear assembly supporting member, and said output shaft being supported solely from said housing side wall.

16. A thread Winding machine comprising a motor, a gainer mechanism, rotatable means for supporting a package adapted to have a thread wound thereon driveconnected to said motor, reciprocable means for guiding a thread onto said package, means including a rotatably mounted cam drive-connected to said motor through said gainer mechanism for reciprocating said thread guiding means, and a housing having a generally vertical side wall and support means at the bottom thereof surrounding said gainer mechanism, said motor, said package supporting means, and said thread guiding means all being supported at one end thereof from said housing side wall 8 with the axial centerlines of said package supporting means, said cam and the output shaft fixed relative to each other.

17. The thread winding machine as defined in claim 1, wherein the means for reciprocating said thread guiding means includes a cam follower and said cam is effective to cause said follower to traverse the length of said cam once in a predetermined plural number of revolutions of said cam.

18. The thread winding machine as defined in claim 1, wherein the means for guiding a thread onto the package includes a cam follower, a thread guide assembly arm, a member reciprocably mounted on a shaft oriented substantially parallel to said package supporting means and fixed to said cam follower, said thread guide assembly arm being pivotally mounted on said reciprocable member.

19. The thread winding machine as defined in claim 1, wherein the means for guiding a thread onto the package includes a thread guide assembly comprising a thread guide, means for biasing aid guide against the thread package, and means for selectively manually varying the force with which said guide is biased against the package.

20. The thread Winding machine as defined in claim 1, wherein the means for guiding a thread onto the package includes an elongated housing having substantially parallel end walls at the opposite ends thereof, said cam being in and extending substantially the length of said housing, bearing means rotatably supporting said cam from said housing end Walls, a guide bar supported by said end walls in parallel spaced relation to said cam, a thread guide assembly support slidable on said guide bar, a cam follower fixed to said support and extending into a cam track formed in the surface of said cam, and a thread guide assembly rotatably mounted on said support and restrained against movement therealong.

21. The thread winding machine as defined in claim 20, including means comprising an integral mounting flange on one end of said elongated housing for supporting the thread guiding means in cantilever fashion from said gainer housing.

22. The thread Winding machine as defined in claim 20 including bearings between said guide bar and said thread guide assembly support to permit free movement of said assembly along said guide bar.

23. The thread Winding machine as defined in claim 20, wherein said elongated housing has an access opening extending substantially its length and including a dust cover fixed over said opening, said dust cover being slotted to permit movement of the cam follower relative to the dust cover.

References Cited by the Examiner UNITED STATES PATENTS 2,079,730 5/1937 Blair 242-18 X 2,116,409 5/1938 Parks 242-18 2,116,410 5/1938 Parks 242-18 2,185,309 1/1940 Pierce 242-158.3 2,252,353 8/ 1941 Pierce 242-45 2,296,959 9/194-2 Swanson 242-45 2,328,344 8/1943 Jones 242-43 X 2,450,187 9/1948 Day 242-43 2,620,999 12/1952 Carter et al. 242-157 2,934,284 4/1960 Steeger 242-158.3 2,970,790 2/1961 Neal 242-157 3,070,319 12/ 1962 Mackie 242-18 3,073,537 1/1963 Mackie 242-18 STANLEY N. GELREATH, Primary Examiner. MERVIN STEIN, Examiner. 

1. A THREAD WINDING MACHINE COMPRISING A MOTOR, A GAINER MECHANISM OPERABLY CONNECTED TO SAID MOTOR, ROTATABLE MEANS FOR SUPPORTING A PACKAGE ADAPTED TO HAVE A THREAD WOUND THEREON DRIVE-CONNECTED TO SAID MOTOR, RECIPROCABLE MEANS FOR GUIDING A THREAD ONTO SAID PACKAGE, MEANS INCLUDING A ROTATABLY MOUNTED CAM DRIVECONNECTED TO SAID GAINER MECHANISM FOR RECIPROCATING SAID 